EP4187127A1 - Transmission hydromécanique et machine de travail agricole équipée d'une telle transmission - Google Patents

Transmission hydromécanique et machine de travail agricole équipée d'une telle transmission Download PDF

Info

Publication number
EP4187127A1
EP4187127A1 EP22196464.6A EP22196464A EP4187127A1 EP 4187127 A1 EP4187127 A1 EP 4187127A1 EP 22196464 A EP22196464 A EP 22196464A EP 4187127 A1 EP4187127 A1 EP 4187127A1
Authority
EP
European Patent Office
Prior art keywords
transmission
bearing
hydrostatic
hydromechanical
bearing bridge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22196464.6A
Other languages
German (de)
English (en)
Inventor
Thomas Gohde
Sebastian Surmann
Helge Stertkamp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Claas Industrietechnik GmbH
Original Assignee
Claas Industrietechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Claas Industrietechnik GmbH filed Critical Claas Industrietechnik GmbH
Publication of EP4187127A1 publication Critical patent/EP4187127A1/fr
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/08—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders
    • F16H39/10—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing
    • F16H39/14—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing with cylinders carried in rotary cylinder blocks or cylinder-bearing members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/028—Gearboxes; Mounting gearing therein characterised by means for reducing vibration or noise
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/20—Off-Road Vehicles
    • B60Y2200/22—Agricultural vehicles
    • B60Y2200/221—Tractors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02091—Measures for reducing weight of gearbox
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the present application relates to a hydromechanical transmission according to the preamble of independent patent claim 1 and an agricultural working machine, in particular a tractor, according to the preamble of independent patent claim 15.
  • a power-split hydro-mechanical transmission traditionally includes a mechanical transmission, such as a planetary gear, and a continuously variable hydrostatic transmission with two hydrostatic units.
  • the two hydrostatic units are connected to each other in a fluid circuit for transmitting a drive power, with one of the hydrostatic units working as a pump and the other of the hydrostatic units working as a motor.
  • the absorption volume or delivery volume of the corresponding hydrostatic unit is varied, a stepless adjustment of the transmission ratio of the hydrostatic transmission is realized. Because the hydrostatic transmission is operatively connected to the mechanical transmission, the hydrostatic transmission affects the speed of an output shaft of the mechanical transmission depending on the gear ratio of the hydrostatic transmission.
  • the hydrostatic units of such hydrostatic transmissions are rotatably mounted in a so-called bearing bridge, which has other functions in addition to its function as a bearing for the hydrostatic units.
  • the bearing bridge of a hydrostatic transmission thus forms a line section of the fluid circuit for transmitting the drive power.
  • a so-called adjusting device is attached or formed on the bearing bridge, which is used for pivoting to change the delivery and/or absorption volume of the hydrostatic units, the bearing bridge for actuating the adjusting device comprising further channels or bores of a further fluid circuit for supplying the adjusting device .
  • the hydrostatic transmission is connected via the bearing bridge to the transmission housing, in which both the mechanical transmission and the hydrostatic transmission are accommodated.
  • a hydrostatic transmission with such a bearing bridge is, for example, from DE 10 2008 008 236 A1 known.
  • the present invention relates to a power-split hydromechanical transmission with a mechanical transmission and a continuously variable hydrostatic transmission that interacts with the mechanical transmission.
  • the mechanical transmission and the hydrostatic transmission are accommodated in a transmission housing of the hydromechanical transmission.
  • the hydrostatic transmission comprises a hydrostatic unit acting as a pump and a hydrostatic unit acting as a motor, which are hydraulically connected to one another to transmit drive power.
  • the hydrostatic transmission includes a bearing bracket in which the hydrostatic units are rotatably mounted.
  • the hydromechanical transmission is characterized in that the bearing bridge is divided into two parts, comprising a first bearing bridge element and a second bearing bridge element.
  • the first bearing bridge element includes channels or bores that are hydraulically connected to an adjusting device of the hydrostatic transmission to change the delivery and/or absorption volume of the hydrostatic units, and the second bearing bridge element includes channels that hydraulically connect the hydrostatic units to transmit the drive power .
  • the hydrostatic units used in connection with the invention can in principle be of different types.
  • at least one, preferably both, of the hydrostatic units is an axial piston machine with a variable delivery or absorption volume. Since one, preferably both, hydrostatic units have a variable delivery or absorption volume, a continuously variable ratio between a hydrostatic unit acting as a pump and a hydrostatic unit acting as a motor can be achieved with a corresponding hydraulic connection of the hydrostatic units by changing the volume of one or both axial piston machines.
  • Various types of adjustable axial piston machines are known and can be used within the scope of the invention.
  • the two-part design of the bearing bracket of the hydrostatic transmission according to the invention has numerous advantages. This reduces the weight of the hydrostatic transmission to a considerable extent, since the bearing bracket only has material at those points where it is actually necessary for the corresponding function to be fulfilled. Due to the arrangement of the channels for the transmission of the drive power, the so-called high-pressure and low-pressure channels, in the second, when the hydromechanical transmission is installed in the agricultural machine, the lower bearing bridge element and the channels or bores, which are connected to the actuating device of the hydrostatic transmission to Changing the delivery and / or displacement volume are hydraulically connected, the so-called control pressure channels or bores, in the first, when installed in the agricultural machine state of the hydromechanical transmission upper bearing bridge element, the complexity of the bearing bridge is reduced to a considerable extent.
  • the manufacture of the bearing bridge can be simplified since the two bearing bridge elements can be manufactured in parallel.
  • the combination of reduced complexity and efficient material distribution in turn ensures that fewer installation space restrictions are created in the area of the bearing bridge, so that an arrangement of further components, for example drive shafts, output shafts and/or cable harnesses of the hydromechanical transmission and/or the agricultural working machine, is more flexible can be done.
  • the bearing bracket comprises two first bearing mounts spaced apart from one another, with axes running centrally through the first bearing mounts being aligned parallel to one another.
  • each first bearing recording elements of the hydrostatic unit are included that are operatively connected to the mechanical transmission by means of a clutch device.
  • the first bearing mounts are spaced apart from one another by means of a web, the division of the bearing bridge running through the web and the first bearing mounts of the bearing bridge.
  • the axes of the first bearing mounts preferably lie in the parting plane.
  • the division in the area of the first bearing mounts allows simplified assembly and maintenance of the hydromechanical transmission. Due to the division of the bearing bridge, the hydrostatic transmission can be connected to the mechanical transmission in a particularly uncomplicated and step-by-step manner. Furthermore, there is good accessibility to the various components of the hydromechanical transmission in the event of maintenance, with only individual elements having to be removed by a maintenance engineer. If the axes running through the first bearing mounts lie in the parting plane, which is a horizontal plane when the hydromechanical transmission is installed in the agricultural working machine, a relatively even power transmission through the bearing bridge in the area of the first bearing mounts is ensured during operation of the hydromechanical transmission. This increases the service life of the hydromechanical transmission.
  • the connection of the first bearing mounts via a web also allows other components to be guided adjacent, in particular above and below the web when the hydromechanical transmission is installed, and thus between the bearing bracket, so that the installation space restrictions are further reduced.
  • the bearing bridge comprises two spaced-apart second bearing mounts and two spaced-apart third bearing mounts.
  • the first bearing bridge element comprises the second bearing mounts and the second bearing bridge element comprises the third bearing mounts.
  • One hydrostatic unit is mounted in each case in a second bearing mount and a third bearing mount so as to be rotatable about a rotation axis or pivot axis.
  • the distribution or allocation of the second and third bearing mounts to the first and second bearing bridge element also serves to divide the function of pivoting and transmission of the drive power between the first and second bearing bridge element, so that each bearing bridge element only has to absorb a proportion of the forces that are generated during operation of the hydromechanical transmission by the Pressures of the hydraulic fluids occur, whereby a relatively even load on the bearing bracket is further favored.
  • the axes of rotation run orthogonally to the axes of the first bearing mounts.
  • an axis of rotation of a hydrostatic unit in each case orthogonally intersects an axis of a first bearing mount.
  • the channels of the second bearing bridge element are formed between the third bearing mounts and hydraulically connect the third bearing mounts to one another.
  • first, second and/or third bearing mounts are each of cylindrical design.
  • the production costs of the bearing bridge can be reduced, since no complicated geometries have to be created and/or connecting elements have to be used, but a geometry that is very easy to produce in terms of production technology is formed, so that the intermediate shafts and components of the hydrostatic units to be stored therein can be directly and/or indirectly, for example using a bearing, can be used in an uncomplicated manner.
  • each hydrostatic unit comprises a swivel housing in which a piston drum is accommodated in a rotatably movable manner.
  • Each hydrostatic unit includes a rotary feedthrough hydraulically connected to the channels of the second bearing bridge element and a pivot pin that can be actuated by means of the actuating device.
  • the swivel and pivot of a hydrostatic unit are formed at opposite ends of the pivot housing of the hydrostatic unit.
  • an axial piston machine in a bent-axis design comprises a piston drum which, from a structural point of view, expediently comprises a rotatable piston housing provided with cylinder bores and pistons inserted therein, which are connected to a drive flange disk in particular via ball joints, with a rotational axis of the piston housing forming a pivoting angle with a rotational axis of the drive flange disk , which can be changed about a pivot axis by pivoting a pivot housing accommodating the piston housing in order to change the delivery and/or absorption volume of the hydrostatic unit.
  • the rotary leadthroughs of the hydrostatic units are mounted in the third bearing mounts and the pivots of the hydrostatic units are rotatably mounted in the second bearing mounts.
  • the hydraulic fluid flowing during operation is either routed very directly from the channels in the second bearing bridge element to the rotary union, depending on the function of the hydrostatic unit or routed from the rotary union to the channels of the second bearing bridge element. This very direct conduction of the hydraulic fluid reduces the occurrence of pressure losses in the high-pressure hydraulic circuit.
  • each hydrostatic unit includes a hydraulically effective damping element.
  • Hydrostatic units cause operational hydraulic pressure fluctuations.
  • these pressure oscillations are caused by the transmission of the mechanical piston movements into the pressure fluid.
  • the pressure oscillations form a pressure wave whose wavelength depends on the frequency with which the pistons impress the pressure oscillation.
  • a stationary pressure wave forms in the channel, in which the transit time of a wave maximum corresponds exactly to the time within which the vibration exciter, i.e. a hydrostatic unit, generates the next wave maximum. This phenomenon causes the wave maxima to continue to intensify and an ever higher pressure amplitude to build up in the channel.
  • damping elements can be hydraulically active devices of various types, with which hydraulic pressure fluctuations within the channels in the second bearing bridge element can be damped.
  • the hydraulically effective damping element is preferably designed as a Helmholtz resonator, lambda/4 hose, hydraulic spring accumulator, active damper or the like.
  • the hydraulically effective damping element is particularly preferably designed as a Helmholtz resonator.
  • a Helmholtz resonator is an acoustic resonator that is essentially formed by a resilient volume that, together with a stub coupled to the channels, forms an acoustic system capable of oscillating with one (or more) specific resonant frequencies. With a suitable design and arrangement of the Helmholtz resonator, it effectively absorbs certain vibration frequencies.
  • a so-called lambda/4 hose can be used as a hydraulically effective damping element.
  • a tube-like element e.g. hose
  • the tube-like element is closed at the end facing away from the channels in order to reflect pressure waves that strike there. Due to the reflection after a quarter of the wavelength, the lambda/4 hose causes a phase shift of the returning wave of 180° compared to the wave in the hydraulic line, so that the wave self-extinguishes.
  • the hydraulically effective damping element is arranged on the outside of the swivel housing of the hydrostatic unit and is hydraulically connected to channels of the hydrostatic unit that hydraulically connect the rotary feedthrough and the piston drum to one another.
  • the hydraulically effective damping element is preferably arranged directly adjacent to the rotary feedthrough on the outside of the swivel housing.
  • the hydraulically effective damping element is particularly preferably hydraulically connected to the channel at the beginning of a channel of the hydrostatic unit close to the piston drum.
  • an antinode wave maximum usually in the immediate vicinity of a hydrostatic unit.
  • the hydrostatic transmission comprises damping elements which flexibly connect the hydrostatic transmission to the transmission housing.
  • the damping elements each include a pin surrounded by an elastic sleeve.
  • the transmission of vibrations from the hydrostatic transmission to the transmission housing can be suppressed by means of the damping elements, as a result of which the transmission housing does not act as a sounding board, or only to a small extent, which radiates the vibrations of the hydrostatic transmission into the environment.
  • the use of trunnions surrounded by an elastic sleeve that dampens the vibrations of the hydrostatic transmission creates a connection between the transmission housing and the hydrostatic transmission that is flexible and strong enough to withstand the forces acting between the hydrostatic transmission and the environment.
  • each damping element is formed integrally with the bearing bracket.
  • the integral configuration of the journals with the bearing bridge creates a structure intended for damping vibrations without weak points that could lead to a failure of the structure during operation of the hydromechanical transmission, since there is no need to fix the journal on the bearing bridge by means of a fit.
  • the damping elements are formed on the second bearing bridge element.
  • the damping elements are aligned parallel to the axes of the first bearing mounts.
  • the arrangement or design of the damping elements on the second bearing bracket element allows the hydrostatic transmission to be connected to the transmission housing in a particularly uncomplicated manner for a fitter. Furthermore, due to the axial arrangement, ie an arrangement along the longitudinal axis of the agricultural working machine during operation, a particularly low noise emission from the hydrostatic transmission to the transmission housing and vice versa is achieved.
  • the hydrostatic transmission has four damping elements.
  • a further one of the four damping elements is arranged at a distance from each of the four damping elements in two spatial directions. All four damping elements are arranged in a plane spanned by the two spatial directions.
  • the plane preferably runs through the third bearing mounts, in particular parallel to the parting plane of the bearing bracket.
  • This arrangement ensures uniform vibration damping and creates only minimal installation space restrictions in the area around the second bearing bridge element.
  • the object according to the invention is also achieved by an agricultural working machine, in particular a tractor, according to independent patent claim 15 .
  • FIG. 1 shows an agricultural working machine 1 in the form of a tractor, in which the power-split hydromechanical transmission 2 according to the invention is used.
  • FIG. 2 shows a schematic and exemplary representation of the hydromechanical transmission according to the invention FIG. 3 can be seen.
  • the hydromechanical transmission 2 includes a shown in FIGS. transmission housing, not shown, in which the mechanical transmission 3 and the hydrostatic transmission 4 are accommodated.
  • Such a hydromechanical transmission 2 forms part of a vehicle drive train in FIG. 1 illustrated agricultural vehicle machine 1 and enables a steplessly adjustable transmission between a transmission input shaft 5 (which can be driven by a drive motor of the agricultural working machine 1, not shown in the figures) and a transmission output shaft 6 (supplying one or more drive axles of the agricultural working machine 1 with drive power) of the hydromechanical transmission 2.
  • the transmission input shaft 5 of the hydromechanical transmission 2 which is not shown, is drive-connected to the drive motor of the agricultural working machine 1 and runs centrally into the hydromechanical transmission 2 .
  • the transmission input shaft 5 lies on a common axis 8 with a power take-off shaft 7 emanating from the hydromechanical transmission 2.
  • the transmission input shaft 5 and the power take-off shaft 7 are connected to one another in a rotationally fixed manner.
  • the speed of the PTO shaft 7 therefore always corresponds at least essentially to the speed of the transmission input shaft 5.
  • the transmission input shaft 5 is part of the mechanical transmission 3 and runs through the hydrostatic transmission 4.
  • the mechanical transmission 3 includes three intermediate shafts 9, 10, 11, each of which leads to the transmission input shaft 5 are aligned parallel, therefore run parallel to the axis of the transmission input shaft 5.
  • Two of the three intermediate shafts 9, 10 are each operatively connected or drive-connected to the hydrostatic transmission 4 of the hydromechanical transmission 2 via a coupling device 12.1, 12.2, each of which preferably comprises a curved tooth coupling.
  • the third intermediate shaft 11 is operatively or drivingly connected to the transmission output shaft 6 .
  • the mechanical gear 3 is designed as a planetary gear, but a detailed description of the planetary gear is omitted below.
  • the planetary gear can be designed as a simple planetary set or as a stepped planetary gear.
  • two of the three intermediate shafts 9, 10 are each operatively connected or drive-connected via a clutch device 12.1, 12.2 to the hydrostatic transmission 4 of the hydromechanical transmission 2, in particular to a so-called hydrostatic unit 13, 14 of the hydrostatic transmission 4.
  • the hydrostatic transmission 4 is used to transmit drive power by a hydrostatic unit 13 acting as a pump; 14 with a hydrostatic unit 14 acting as a motor; 13 is hydraulically connected.
  • the hydrostatic unit 13 is assigned to the intermediate shaft 9 and is operatively or drivingly connected to it via the clutch device 12.1.
  • the hydrostatic unit 14 is assigned to the intermediate shaft 10 and is operatively connected to it via the clutch device 12.2. drive connected.
  • the two hydrostatic units 13, 14 are hydraulically connected to one another via hydraulic lines 15, 16 for the transmission of the drive power. In this way, each acting as a pump hydrostatic unit 13; 14 drive power to the hydrostatic unit 14 acting as a motor; 13 transferred. In relation to the intermediate shafts 9, 10, this hydraulic coupling via the pump and motor acts like a gear, which produces a rotational speed coupling between the intermediate shafts 9, 10.
  • this hydraulic coupling via the pump and motor acts like a gear, which produces a rotational speed coupling between the intermediate shafts 9, 10.
  • the hydrostatic units 13, 14 are so-called axial piston machines in a bent-axis design, each comprising a swivel housing 17, 18, which rotates about an axis, i.e. a rotational axis 19 of the respective hydrostatic unit 13, in order to change a delivery and/or absorption volume , 14, pivots.
  • By using such configured hydrostatic units 13, 14 can be with the hydrostatic transmission 4 in a simple manner-namely by changing the delivery and/or absorption volume-variably adjust a speed ratio that exists between the hydrostatic units 13, 14 and thus between the intermediate shafts 9, 10 that are operatively or drive-connected thereto.
  • the hydrostatic transmission 4 can be operated in a reversible direction, i.e. the functional assignment of the hydrostatic units 13, 14 as a pump and motor is reversible .
  • hydrostatic unit 13, 14 shown in detail includes a shown in FIGS. piston drum, not shown, which comprises a rotatable piston housing provided with cylinder bores and pistons inserted therein, which are each connected via a ball joint to a wheel-shaped drive flange disk.
  • piston drum not shown
  • the axis of rotation of the piston housing forms with an axis of the drive flange disk, which in each case coincides with an axis of one of the intermediate shafts 9, 10 accommodated in the coupling devices 12.1, 12.2, in each case a pivoting angle which can be changed by pivoting a pivoting housing 17, 18 accommodating the piston housing , so as to change the delivery and/or absorption volume of the hydrostatic units 13, 14.
  • a rotary leadthrough 20 is provided on the swivel housing 17, 18 cylindrical basic shape and a pivot 21 also formed with a cylindrical basic shape, which define the axis of rotation or pivot axis 19 of each hydrostatic unit 13, 14.
  • the swivel housing 17, 18 is accommodated or mounted by means of the pivot pin 21 and the rotary bushing 20 in relation to a bearing bridge 22 of the hydrostatic transmission 4, which will be described in detail below, the swivel housing 17, 18 can be rotated in relation to the bearing bridge 22 about the axis of rotation or Pivot axis 19 pivot.
  • the pivot pin 21 is a purely mechanical element that is actuated by means of an in FIG. 2 to be seen adjusting device 23, which is also received or mounted on the bearing bridge 22, is actuated in order to pivot the hydrostatic unit 13, 14 or the pivot housing 17, 18 of the hydrostatic unit 13, 14.
  • the rotary feedthrough 20, in addition to a mechanical function as a pivot bearing journal, also has the function of ensuring the hydraulic supply at the transition between the bearing bridge 22 and the pivot housing 17, 18 (which can be moved relative to it).
  • each hydrostatic unit 13, 14 are formed or arranged at a distance from one another at opposite ends of a pivot housing 17, 18 of a hydrostatic unit 13, 14, so that a rotational axis or pivot axis 19 of the hydrostatic unit 13, 14 respectively centrally through the pivot 21 and the rotary union 20 of a hydrostatic unit 13, 14 runs.
  • the rotary feedthrough 20 comprises two peripheral regions 24, 25 which are axially spaced apart from one another, openings in the form of elongated holes extending in the peripheral direction being formed on each of these peripheral regions 24, 25.
  • the bearing bridge 22 two in the FIGS. not shown are formed according to axially spaced annular recesses, so that in cooperation between the hydrostatic units 13, 14 and the bearing bracket 22 hydraulic connections are created, which are part of the two hydraulic lines 15, 16.
  • the hydrostatic transmission 4 includes the bearing bridge 22, the particular FIGs. 4A to 4C can be seen.
  • the hydrostatic units 13, 14 are accommodated or stored.
  • the bearing bridge 22 includes, among other things, two first bearing mounts 26.
  • the two first Bearing mounts 26 are spaced apart from one another.
  • An axis 27 runs centrally through each of the first bearing mounts 26, which axis coincides with an axis of the intermediate shafts 9, 10 in each case.
  • the two axes 27 of the two first bearing mounts 26 are aligned parallel to one another, and therefore run axially parallel to one another, specifically at a distance d1 from one another.
  • the first bearing mounts 26 are arranged spaced apart from one another in a direction y, which runs orthogonally to a direction x of the agricultural working machine 1, which defines the main direction of extent of the agricultural working machine 1, and the two axes 27 each run in Direction x, ie the main extension direction, of the agricultural working machine 1 at a distance d1 from one another.
  • the two first bearing seats 26 are structurally connected to one another via a web 28 which is part of the bearing bracket 22 .
  • the bearing bridge 22 also includes two second bearing mounts 29 and two third bearing mounts 30.
  • the two second bearing mounts 29 are also spaced apart from one another. The same applies to the third bearing mounts 30.
  • the second and third bearing mounts 29, 30 are arranged opposite one another at a distance from one another, specifically at a distance d2.
  • the two second and third bearing mounts 29, 30 are used to rotatably accommodate or mount the hydrostatic units 13, 14, with a second bearing mount 29 and a third bearing mount 30 together receiving or mounting one of the two hydrostatic units 13, 14 in a rotatable manner.
  • the pivot 21 of a hydrostatic unit 13, 14 is rotatably accommodated or mounted in a second bearing mount 29 and the rotary leadthrough 20 of the same hydrostatic unit 13, 14 in a third bearing mount 30.
  • Each hydrostatic unit 13, 14 is therefore accommodated or mounted in a second and a third bearing mount 29, 30 by means of its pivot 21 and its rotary bushing 20 so that it can rotate about its axis of rotation or pivot axis 19, with each axis of rotation or pivot axis 19 passing centrally through the respective second and third bearing mount 29, 30 runs.
  • the axes of rotation or pivot axes 19 run orthogonally to the axes 27 of the first bearing mounts 26, preferably one axis of rotation or pivot axis 19 intersects one of the axes 27 orthogonally, so that a distance between the axes of rotation or pivot axes 19 corresponds to the distance d1.
  • a second and third bearing mount 29, 30 provided for the storage of a hydrostatic unit 13, 14 can thus be moved in a z direction, which is orthogonal to the x direction and orthogonal to the y direction agricultural working machine 1 runs, with the distance d2 spaced apart from one another arranged opposite one another.
  • the two rotational axes or pivot axes 19 also run in the z direction, and the two second bearing mounts 29 and the two third bearing mounts 30 are spaced apart from one another in the y direction.
  • the first, second and/or third bearing mounts 26, 29, 30 are each cylindrical, with the first bearing mounts 26 in particular being able to have gradations in the direction of their axes 27, which are used to accommodate and position bearings for storing or receiving the means of the respective Coupling device 12.1, 12.2 with the intermediate shafts 9, 10 operatively connected elements of the hydrostatic units 13, 14 are used.
  • the bearing bridge 22 is designed in two parts, comprising a first bearing bridge element 22.1 and a second bearing bridge element 22.2.
  • the two bearing bridge elements 22.1 and 22.2 are particularly in the FIGs. 4B and 4C shown.
  • Both the first bearing bridge element 22.1 and the The second bearing bridge element 22.2 each comprise hydraulic channels 31, 32.
  • the first bearing bridge element 22.1 comprises the hydraulic channels or bores 31, which are hydraulically connected to the actuating device 23 of the hydrostatic transmission 4 for changing the delivery and/or absorption volume of the hydrostatic units 13, 14 .
  • the second bearing bridge element 22.2 comprises the hydraulic channels 32, which hydraulically connect the two hydrostatic units 13, 14 to one another in order to transmit the drive power, and accordingly form line sections of the hydraulic lines 15, 16.
  • each bearing bridge element 22.1, 22.2 can also have corresponding connections in order to supply hydraulic fluid to the respective hydraulic circuit (ie hydraulic circuit for the control pressure and hydraulic circuit for the transmission of the drive power).
  • FIGs. 4A to 4C to see the division of the bearing bridge 22 runs through the first bearing mounts 26 and the web 28, wherein, preferably, the axes 27 of the first bearing mounts 26 lie in the parting plane.
  • the first bearing mounts 26 are thus formed in at least substantially equal proportions by the first and second bearing bridge element 22.1, 22.2.
  • the first bearing bridge element 22.1 also includes the two second bearing mounts 29, in which the pivot pins 21 of the hydrostatic units 13, 14 are received or mounted so that they can rotate, as well as further bearing mounts 33, which are used to hold cylinders 34 of the actuating device 23 for actuating the pivot pins 21 .
  • the second bearing bridge element 22.2 also includes the third bearing mounts 30, in which the rotary leadthroughs 20 of the hydrostatic units 13, 14 are received or mounted in a rotatably movable manner.
  • the channels 32 of the second bearing bridge element 22.2 are defined by two separate channels 32, one channel 32 forming a line section of the hydraulic line 15 and one channel 32 forming a line section of the hydraulic line 16, whereby the channels 32 correspond to the function of the hydrostatic units 13 , 14 function as line sections of the high-pressure side or the low-pressure side.
  • the two channels 32 of the second bearing bridge element 22.2 are arranged such that they are between the two third bearing mounts 30, the two third bearing mounts 30 hydraulically connecting to each other, are formed.
  • the bearing bracket 22 comprises in a region accommodating the rotary feedthrough 20, i.e.
  • the third bearing mounts 30, two corresponding annular recesses spaced axially apart, so that in the interaction between the hydrostatic units 13, 14 and the bearing bracket 22 or the second Bearing bridge element 22.2 hydraulic connections are created, which are part of the two hydraulic lines 15, 16.
  • the channels 32 are therefore hydraulically connected to the annular recesses in the third bearing mounts 30, which in turn are hydraulically connected to the openings of the rotary unions 20, so that drive power is transmitted between the hydrostatic units 13, 14 during operation of the hydromechanical transmission 2.
  • Each hydrostatic unit 13, 14 also includes a hydraulically effective damping element 35, which serves to avoid operating noises that can arise during operation of the hydrostatic transmission 4, at least in certain operating situations.
  • the hydraulically effective damping elements 35 are each formed on the swivel housing 17, 18 of a hydrostatic unit 13, 14, specifically on the outside of the swivel housing 17, 18, preferably on the outside of the swivel housing 17, 18 directly adjacent to the rotary feedthrough 20 of the hydrostatic unit 13, 14.
  • the hydraulically effective damping element 35 is therefore spatially formed between the pivot 21 and the rotary feedthrough 20 as part of the pivot housing 17, 18 of a hydrostatic unit 13, 14.
  • the hydraulically effective damping element 35 is formed in the pivot housing 17, 18, shown in FIGS. Channels, not shown, which hydraulically connect the rotary feedthrough 20 to the piston drum and thus form a further line section of the hydraulic lines 15, 16, hydraulically via a line also shown in the FIGS. not shown connected stub.
  • the hydraulically effective damping element 35 is preferably designed as a so-called Helmholtz resonator, with a description of the mode of operation being omitted below since the mode of operation of such a hydraulically active damping element in the context of hydrostatic transmissions is well known.
  • hydraulically effective damping element 35 can also be used as the hydraulically effective damping element 35, such as a lambda/4 hose, a hydraulic spring accumulator or an active damper.
  • the hydrostatic transmission 4 also includes damping elements 36, which connect the hydrostatic transmission 4 to the transmission housing of the hydromechanical transmission 2 connect compliantly.
  • the damping elements 36 serve to decouple the hydrostatic transmission 4 from the transmission housing in terms of vibrations.
  • the damping elements 36 are each as shown in FIGS. not shown elastic sleeve surrounding pin 37 is formed.
  • the pin 37 of a damping element 36 is preferably formed integrally with the bearing bridge 22 and has a cylindrical shape. However, the pin 37 can also be connected to the bearing bracket 22 by means of a fit.
  • the elastic sleeve is preferably designed as a so-called ultra bushing, which in a manner known per se has an elastomer layer between rigid outer and inner sleeves.
  • the ultra socket is fixed to the pin 37 by clamping.
  • the pin 37 surrounding the ultra socket is fixed to the transmission housing via a non-positive and/or form-fitting fit, preferably using a cover, with an elastomer disc being able to be arranged between the pin 37 and the transmission housing, which can be slightly compressed in the axial direction of the pin 37.
  • This elastomer disc together with the ultra bush favors a damped oscillating movement of the pin 37 relative to the transmission housing in all three spatial directions, i.e. the x direction, the y direction and the z direction when the hydromechanical transmission 2 is installed in the agricultural working machine 1.
  • the damping elements 36 are formed on the second bearing bridge element 22.2, preferably integrally with the second bearing bridge element 22.2.
  • Axles 38 running centrally through the pins 37 are aligned parallel to the axes 27 of the first bearing mounts 26 .
  • the axes 38 of the pins 37 run axially parallel to the axes 27 of the first bearing mounts 26.
  • damping elements 36 are preferably arranged on the bearing bridge 22, in particular on the second bearing bridge element 22.2.
  • the damping elements 36 are each formed in the corner regions of the second bearing bridge element 22.2, at the height (direction z when the hydromechanical transmission 2 is installed in the agricultural working machine 1) of the third bearing mounts 30.
  • a further one of the four damping elements 36 is arranged at a distance from each damping element 36 in two spatial directions. All four damping elements 36 are arranged in a plane spanned by the two spatial directions, the plane running through the third bearing mounts 30 .
  • the plane is defined by the x direction and the y direction spanned, the plane therefore runs parallel to the parting plane of the bearing bridge 22 through the third bearing mounts 30.
  • the damping elements 36 are arranged adjacent to one another in the x and y directions, with the pins 37 each of two damping elements 36 that are adjacent in the direction y, each starting from the second bearing bracket element 22.2 in the negative or positive direction x, ie the main direction of extension, of the agricultural working machine 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Motor Power Transmission Devices (AREA)
EP22196464.6A 2021-11-22 2022-09-20 Transmission hydromécanique et machine de travail agricole équipée d'une telle transmission Pending EP4187127A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021130502.0A DE102021130502A1 (de) 2021-11-22 2021-11-22 Hydromechanisches Getriebe sowie landwirtschaftliche Arbeitsmaschine mit einem solchen Getriebe

Publications (1)

Publication Number Publication Date
EP4187127A1 true EP4187127A1 (fr) 2023-05-31

Family

ID=83398246

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22196464.6A Pending EP4187127A1 (fr) 2021-11-22 2022-09-20 Transmission hydromécanique et machine de travail agricole équipée d'une telle transmission

Country Status (2)

Country Link
EP (1) EP4187127A1 (fr)
DE (1) DE102021130502A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10008965A1 (de) * 1999-02-26 2001-03-15 Sauer Inc Einteilige Jochhubverstellvorrichtung für hydraulische Pumpen und verstellbare Motoren in Schrägachsenbauart
DE102008008236A1 (de) 2008-02-08 2009-08-13 Markus Liebherr International Ag Hydrostatisch leistungsverzweigtes Getriebe
US20100018201A1 (en) * 2008-07-22 2010-01-28 Yasuhisa Mochizuki Hydrostatic Transmission
DE102012004073A1 (de) * 2011-03-25 2012-09-27 Claas Industrietechnik Gmbh Hydromechanisches Getriebe
EP2960547A1 (fr) * 2014-06-27 2015-12-30 CLAAS Industrietechnik GmbH Système d'engrenage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10008965A1 (de) * 1999-02-26 2001-03-15 Sauer Inc Einteilige Jochhubverstellvorrichtung für hydraulische Pumpen und verstellbare Motoren in Schrägachsenbauart
DE102008008236A1 (de) 2008-02-08 2009-08-13 Markus Liebherr International Ag Hydrostatisch leistungsverzweigtes Getriebe
US20100018201A1 (en) * 2008-07-22 2010-01-28 Yasuhisa Mochizuki Hydrostatic Transmission
DE102012004073A1 (de) * 2011-03-25 2012-09-27 Claas Industrietechnik Gmbh Hydromechanisches Getriebe
EP2960547A1 (fr) * 2014-06-27 2015-12-30 CLAAS Industrietechnik GmbH Système d'engrenage

Also Published As

Publication number Publication date
DE102021130502A1 (de) 2023-05-25

Similar Documents

Publication Publication Date Title
DE102006025347B3 (de) Hydromodul mit zwei integrierten Schrägscheiben- oder Schrägachsentriebwerken
DE60220613T2 (de) Getriebe für ein Arbeitsfahrzeug und Fahrzeug
DE102009006909B4 (de) Axialkolbenmaschine mit reduzierter Stelldruckpulsation
DE102007033008B4 (de) Hydrostatisches Getriebe mit zwei Axialkolbentriebwerken
DE102005044956A1 (de) Breitstreckwalze
DE2539029A1 (de) Getriebe zur verwendung als kraftuebertragungskupplung
DE102005017754A1 (de) Baumaschine insbesondere Strassenfräsmaschine, Recycler oder Stabilisierer, sowie Antriebsstrang für derartige Baumaschinen
DE102011116429A1 (de) Stelleinrichtung zum variablen Einstellen wenigstens eines Verdichtungsverhältnisses einer Verbrennungskraftmaschine sowie Verbrennungskraftmaschine
EP2960547B1 (fr) Système d'engrenage
DE2815632A1 (de) Geraeuschgedaempfter hydrogetriebe- antrieb
EP4187127A1 (fr) Transmission hydromécanique et machine de travail agricole équipée d'une telle transmission
DE102004030046B4 (de) Hydrostatisches Schrägachsenmodul mit mehreren Jochen
EP2503190B1 (fr) Engrenage hydromécanique
EP4184037A1 (fr) Transmission hydromécanique et machine de travail agricole équipée d'une telle transmission
DE10021485B4 (de) Hydrostatische Maschine
DE102006045490A1 (de) Aktiver Kraftfahrzeugstabilisator mit eingebautem Aktuator
EP2503195B1 (fr) Limitation de la pression de gavage pour une transmission hydrostatique
DE102004030147A1 (de) Hydrostatisches Schrägachsenmodul mit mehreren Jochen
DE102005021029A1 (de) Axialkolbenmaschine in Schrägscheibenbauweise mit Lagerung des Zylinderblocks auf einem Tragzapfen
DE102012004073A1 (de) Hydromechanisches Getriebe
EP2337949A2 (fr) Agencement de positionnement hydraulique d'un excentrique pour le réglage d'une cylindrée prédéterminée sur un moteur hydrostatique
DE4340310C2 (de) Lageranordnung, insbesondere für Motoren, Getriebe und/oder Fahrerhäuser von Kraftfahrzeugen
DE102008039543B4 (de) Rollenmühle
EP2503189B1 (fr) Engrenage hydromécanique
DE19957568B4 (de) Anordnung mit einem Schwungrad und einer hydrostatischen Axialkolbenmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230601

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20231130

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20240513

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3